Automatic lathe or screw machine



y 1950 c. E. MILLER 2,506,515 AUTOMATIC LATHE 0R SCREW MACHINE Filed May 6, 1944 9 Sheets-Sheet 1 Ill /f/ 7f w f7 17 14 y 1950 c. E. MILLER 2,506,515

AUTOMATIC LATHE OR SCREW MACHINE Filed May 6, 1944 9 Sheets-Sheet 2 May 2, 1950 c. E. MILLER AUTOMATIC LATHE 0R SCREW MACHINE 9 Sheets-Sheet 3 Filed May 6, 1944 May 2, 1950 c. E. MILLER 7 AUTOMATIC LATHE 0R SCREW MACHINE 9 Sheets-Sheet 4 Filed May 6, 1944 \1 3 T W sh w m 3 F M a R Yin" f 3 V a M a Q W Q X A mm 3 QM @Q 2 N. v Q Q o 0 O O Y w 7 F M7 k be QN May 2, 1-950 0. E. MILLER 2,506,515

AUTOMATIC LATHE 0R SCREW MACHINE Filed May 6, 1944 9 Sheets-Sheet 5 May 2, 1950 c. E. MILLER 2,506,515

AUTOMATIC LATHE 0R SCREW MACHINE Filed May 6, 1944 9 Sheets-Sheet 6 May 2, 1950 c. E. MILLER AUTOMATIC LATHE 0R SCREW MACHINE 9 Sheets-Sheet 7 Filed May 6. 1944 firm if May 2, 1950 c. E. MILLER AUTOMATIC LATHE 0R SCREW MACHINE 9 Shee'ts-SheetB Filed May 6. 1944 C. E. MILLER AUTOMATIC LATHE 0R SCREW MACHINE May 2, 1950 9 Sheets-Sheet 9 Filed May 6, 1944 Patented May 2, 1950 AUTOMATIC LATHE OR SCREW MACHINE Carroll E. Miller, Windsor, Vt., assignor to Cone Automatic Machine Company Inc., Windsor, Vt., a corporation of Vermont Application May 6, 1944, Serial No. 534,504

6 Claims.

This invention relates to automatic lathes and screw machines, and more particularly to such machines of the single spindle type where machining operations are performed on a single work bar.

One object of this invention is to provide for a considerable number of machining operations to be performed simultaneously, overlapping, or sequentially, or any combinations of these, without the necessity of stopping to index the work from one to a succeeding tooling station. This means that each tooling operation may be completed without interruption.

As shown herein there are four side forming tool positions, and there are five axial tool positions for turning, drilling, boring, reaming, tapping, or the like.

A further object is to provide controlling mechanism for the axial positioned tools permitting great flexibility of control.

Still another object is to provide an indexing turret for carrying the axial position tools, together with improved indexing and axial motion control mechanism.

Still another object is to provide for control of the axial tooling position tools for operation as desired, either independently of or in definite relation to side forming operations as may be found desirable in any given set up.

A further object of the invention is to provide novel actuating mechanism for the axial position tools including an actuating lever in which the position of the fulcrum as well as of the actuating arm is varied and controlled.

Another object of the invention is to employ a lever for actuating the axial tools wherein the relatively slow cutting motion of these tools is produced by motion of the lever actuating arm, while the relatively fast idle motions are produced by motion of the lever fulcrum.

Another object of the invention is to provide control for the speed varying means which autoit matically locks against actuation all but the parts to be actuated when a change of speed or direction of rotation is desired.

Further objects and advantages will appear from a more complete description of an embodiment of the invention shown in the accompanying drawings, in which Figure 1 is a fragmentary front elevation of a machine embodying the invention.

Figure 2 is a top plan view of the same with the top cover removed and with certain parts shown in section.

Figure 3 is a left hand end elevation of the machine with a lower portion broken away.

Figure 4 is a view partly in front elevation and partly in longitudinal section on line 4-4 of Figure 2.

Figure 5 is a sectional view to a larger scale on line 5-5 of Figure 4.

Figure 6 is a sectional view on line 66 of Figure 5.

Figure 7 is a sectional view to a larger scale on line 1-l of Figure 4.

Figure 8 is a sectional view on line 8-8 of Figure 7.

Figure 8a is a detail sectional view on line 8a 8a of Figure '1, but showing the shaft 409 rocked out of neutral position.

Figure 9 is a sectional view to a larger scale on line 99 of Figure 4.

Figure 10 is a sectional view on lines lll-|ll of Figures 3 and 9 and to the scale of Figure 9.

Figure 11 is a sectional view to a larger scale on line ll-l I of Figure 4.

Figure 12 is a fragmentary front elevation to a larger scale than Figure 1 and showing the stock stop in operative position.

Figure 13 is a sectional view to a larger scale on line l3-|3 of Figure 4.

Figures 14 and 15 ar fragmentary sectional views on lines 14-44 and |5l5, respectively, of Figure 13, Figure 15 being to a larger scale.

Figure 16 is a right hand end elevation of the upper portion of the machine with the end cover removed.

Figure 1'? is a view similar to a portion of Figure 16, but showing the parts in difierent positions.

Figure 18 is a fragmentary exploded perspective view of the tool-holding turret, a bearing therefor, and a tool slide.

Figures 19, 20 and 21 are somewhat diagrammatic views similar to a portion of Figure 4, but showing the parts in successive positions during a cycle of operations of an axial tool.

The machine shown in the drawings comprises a bed I from opposite ends of which arise. hollow columns 2 and 3 connected at their upper ends by a longitudinal frame 4. The upright col- 3 umn 2 has journaled therein and arranged longitudinally of the machine, a work spindle 5.

Axial tool turret Beneath the work spindle and parallel thereto is journaled a shaft 6 which extends into the column 3. Within the column 3 and concentrio to the shaft 6 there is journaled in the end frame members ill and l l of this column, a turret i2 having end flanges l3 and i l connected at angular intervals by webs 45. To the end flange 63 there is secured, as by screws is, an extension El, which, except at its extreme lefthand por tion, is formed pentagonal cross section, each of the sides as shown in Figure 18 being provided with a way is extending longitudinally thereof and having retaining strips I9 holding therein, slidably mounted, a tool holder 26. The end flange iii of the main turret is recessed opposite to these ways so that the holders 2% may extend therethrough. The outer end portion of each holder 25 is narrowed as at 2! and has secure-:1 thereto an extension block 22 provided with an upturned end flange 23' defining, with the end of the extension El, a slot 24. Ea'ch'block 22 is slid able alonga pad 25 on the outer face of the cen tral portion of the turret 12. This turret i2 is also provided with a pair of spaced circular flanges 2's and: 28, eachof which is provided with registering notches- 29 and 39, respectively, through which the block 22 and the portion 2! of the tool holder may slide, the space between these flanges 29 and 39 being substantially the smeas the width" of theslot r4. 7

Between the flanges 29 and 33 011 opposite sides of the'central vertical plane of the machine there are positioned a, pair of journal standards 32 having opposed arcuateflanges 33' shaped to engage between theturret flanges 2? and 28'. The upper endsof these arcuate fl'ahgesiis are-spaced apart as at 34 by an amount substantially ecfaal to the widthsof the SlOts'Z-Q amuse; and also the widths of the block 22 and the portion 21' 'of'e'a-cli tool holder, so that the tool h'old'er in the upper"- most position at any onetime is free to be moved axially between the upperends of the arcuate flanges 33;; while in another angular positions of the turret, these flanges 33 extend through the slots 2t of the h'olders 'andprevent them from being moved axially. Each of the holders 23, as shown in Figure 11', i's 'prov-ide'd with suitable means, suchas a, 1'- slot All, for securementthere to of suitable tools. For example, in Figures 1 ands, a holders! for a-d'rillliZ is show'n as secured to the uppermost holder slide 28. Such tools are arranged in su'ch relation to the axis of work carried by th'e workspindle astoper form the desired operation thereon, but for convcnience herein they are termed the endworking tools, since their motion is lengthwise of the work, due to the sliding motion of their respective holder slides 28. V

The shaft 6- is jo'urnal'ed within the turret 12 so that the turret and its extension H and the shaft 6 mutually support each other during 1 considerable portion'of thel'ength of the shaft The turret 12 which carries the longitudinally movable tool holders is arranged to be indexed to bring the tool holders on the several holder slides successively into operative relation to the work.

' Side working too'ls During the complete cycle of operations on the Work other tools, carried byf our tool holding slides '50, 51, 52' and 53* are arranged to a proach the work from different directions but without capability of axial motion relative thereto. Thus the tool holder at 50 may have the rough forming tool; the tool holder at 5! facing tools; the tool holder 52, the finish forming tool, and the tool holder 53, the cutting off tool. The tool holders lifi and 53 are supported between the end columns 2' and 3 frorhthe'top ,fr aine men her 4 for downward and inward, and upward and outward sliding motion, while the tool holders 5i and 52 are arranged to be moved in from b'ackand front'o f the machine, respectively.

Work spindle and control The upper frame" member 4 supports a main cam shaft 6Q. which is journaled parallel to the spindle 5 and to the lower shaft 6, and this cam shaft 50 supports a series of cam drums which in general control the cycle of operations of the machine; The work 'spindle ma'y be of well known type, having" meanssuoh as; a. collet-chuck for gripping the work and feed mechanism for feed;- ing the work periodically and after the com-- pletion and the cutting 01f of work from the forward end of the stock, these being of the general type well known in theart' It, is sufficient for present purposes to point outthatthe opening and closing of the collet is produced by axial motion of a, spool 6 {surrounding the spindle and mechanisms may be of well known form, no fu-rther description thereof; is; believed necessary. The outer end of thespindle is, supported on a stationaryyoke $8 ,which'supports the weight of stock when thestock is too short to be supported by the usual stock reel (not shown).

Side tool actuating mechanism 7 The four sidet'o'ol sudesar e actuated by cams on certain of .th'e' carndljurhsjcarried by the shaft A5 shown, for "example in Figure 11, the slide ears actuated by the mngituuina rhotion of a bar l9. This bar is provided. with a cam follower rents (see Figur e 2) actuated by cams onla, caindrum l3. fIhe tool slide 531a actuated by the longitudinal mou r a bar it provided witha' 'camlfollowel roll 15' actuated byc'anis on the drum '36. The tool slide 5! [is actuated bythe rocking of a vertical shaft 11, the lower end'of which is connected through a suitable rock arlin with theslide 5! as shown dottedlines" in Figure. 2. I The uppe end of the shaft 11 has fixed thereto an arm 18' to' which is" connected alink lil whicliis corihected to an axially movab e parse at its ear end provided with a cam fo owerfil for actuation by cams on yhe cam d uni 82., rhetsel suds 52 1s similarly a;etu'a ;t' ed by I the rocking of a vertical. shaft thelower en'dfof which is c'onne'cted by a link as to the slide 52 and the upper en'd'orwmcnhas secured thereto an arm 8.4 connected through a link '85 with a slide bar '85 provided with a cam T4, are operatively con} the main control cam shaft 60.

Stock stop A cam drum 90 on the cam shaft 60 is provided with cams which actuate a stock stop which is brought down in front of the work spindle whenever stock is to be fed forward to measure off a length of stock for the next series of machining operations after a completed length has been cut off. As shown best in Figures 2, 4, and 12, the stock stop is carried by a rock shaft 95 which is journaled and slidably mounted in a fixed bearing 96 secured to the lower face of the frame member 4 and at its opposite end is rockably mounted in a slide 91 carrying a cam follower 98 controlled by cams on the cam drum 90. The stock stop 99 is carried at one end of an arm I which is adjustable lengthwise of the shaft 95 by adjustment of a pair of spaced collars i0! and I02 threaded on this shaft at opposite sides of the arm I00. The rear end of the shaft 95 has secured thereto a spiral gear $05 which meshes with a fixed angular rack I01 secured to the under face of the frame member 4, the arrangement being such that as the slide 01 is moved axially toward the stock projecting from the forward end of the spindle, the shaft 95 is rocked to bring the stock stop from an inoperative elevated position down into alinement with the stock into the position shown in Figure 12, so that the stock may be fed out into contact therewith and then clamped, whereupon the stock stop is immediately returned to its upper position with a component of motion axially away from the stock, so that it immediately frees itself therefrom.

Axial tool indenting and actuating mechanism The main control cam shaft 60 carries within the end column 3, a cam drum I carrying on its face a plurality of edge cams as I2I, and opposite to the working edges of these cams, the drum I20 is provided with an outstanding rim I22. Positioned between the rim I22 and the active faces of these cams rides a cam follower I23 projecting inwardly from the actuating arm of a lever I24. This lever I24 is fulcrumed as at I25 on a slide I26 mounted in guides I21 and I28 to move in a path substantially parallel to The lower end of the lever I24 carries a follower I which is adapted to engage in the slot 24 of that particular tool carrier 20 which happens to be uppermost in any indexed position of the turret I2 so that on rocking of the lever I24 from the position shown in Figure 20 to that of Figure 21, the

tool holder 20 may be moved toward the Work to present the tool or tools thereon adjacent to cutting relation to the work. Further motion of the tool holder is produced by engagement of the particular edge cam I2I which happens to tool produced by motion of its fulcrum is a relatively fast idle motion, while the slow working motion is produced by the action of a cam I2I while the lever fulcrum is stationary in the position of Figures 4 and 15. It will be understood that there is a cam I2I for each of the tool holders 20, the main control shaft 60 rotating once for each complete cycle of the machine, during which cycle each of the tool holders 20 is brought into operative position. In the positions of the parts shown in Figures 4, 15, 19 and 21, the slot 24 is out of alinement with the space .between the flanges 29 and 30 of the turret, this I,

.be active at that particular time on the follower .I23 as shown in Figure 4. The motion of the being possible because the arcuate flanges 33 do not prevent such motion of the uppermost tool holder 20. When the tool has completed its work, the corresponding tool holder 20 is retracted quickly to the position shown in Figure 20 with its slot 24 in alinement with the space between the flanges 21 and 28, this being accomplished by motion of the fulcrum slide I26. For this purpose the slide I26 is provided with a cam follower I35 (Figures 13 and 15) which rides in a cam groove I36 in a cam I31 secured to a secondary shaft I38.

During the time that the lever I24 is being moved relatively slowly by the edge cams to cause an axial tool to operate on the work, the cam follower I35 is at the forward limit of its cam groove I36 in the position shown in Figures 4 and 15, and at this position there bears against the cam follower I35 a hardened removable wear plate I40 set into the cam I31 in position to take the thrust exerted by the follower I35 thereagainst. The shaft I38 which carries the cam I31 is rotated by power and its rotation is initiated under control of the main control cam shaft 60. The power for rotating the shaft I38 is derived from a motor I45, the shaft I46 of which (see Figure 14) carries a sprocket wheel I41 over which passes a chain I48. This chain I48 passes beneath a spring pressed idler I49 and over a sprocket wheel I50 journaled on a cross shaft I5I. The chain I48 also passes downwardly about a sprocket wheel I52 carried by a shaft I53 near the base of the machine. This shaft I53 is connected to drive a coolant pump and a lubricating pump, neither of which is shown in the drawings, but which may be located outside the main casing and beneath the motor I45.

The sprocket wheel I50 may be connected to rotate the shaft I5I by means of a clutch I55 (Figures 13 and 14) which may be operated by a bell crank lever yoke I56, the short arm I51 of which is pivoted to the lower end of a link I58, the upper end of which is pivoted at I59 on a, rock arm I60. The link I58 has a pair of spaced follower rolls I62 and I63 between which is positioned a pentagonal cam I64 carried by a shaft I65, the arrangement being such that a this cam I54 is rotated from the position shown in Figure 13, it lifts the link I58 as a high point of the cam rides beneath the follower I62 and throws in the clutch I55, thus to drive the shaft I5I, while when the high point of the cam 564 rides out from the follower I62 and another high point rides above the follower I63, the link I58 is lowered and the clutch I55 is thrown out. The shaft I5I carries a worm I5I0 meshing with a worm wheel I5I I connected as through a shear pin I5I2 with the cam I31 (see Figure 15) so that when ever the clutch I56 is closed, the cam 131 is rotated, this rotation being through a complete revolution, returning the cam follower I35 to its initial extreme left hand position shown in Figure 15 before the rotation of the shaft I38 stops.

The shaft I65 which carries the clutch controlling cam I64 is arranged to be rotated step by step, the step which is effective to close the clutch I55 being produced by actuation of the main control shaft 60, while the step which opens the clutch I 55 is accomplished by the rotation of the secondary shaft I 38. For the purpose of effecting closing of the clutch I55, the main control shaft 60 has adjustably secured to its outer end, five disks I10 each provided with an outstanding arm I1I, there being one of these arms III corresponding to each of the five faces of the turret. As shown,

each f: the disks its is arranged to beclampedi to the shaft 60, being split with the split ends connected'by adjustable screws, and in order to faclose angular positioning of the arms HI and each may also be provided with an index mark I15, which together with the indexing disk- I12, will facilitate the adjustment of these arms angularly to the esired positions. These arms I -II- are onset relatively into adjacent planes and are arranged in the same pianes with fingers H8 outstanding from a hub member I86 secured tothe shaft E65. The arrangement is such that'as the main control shaft 53 is rotated, these arms I'It may impinge upon the corresponding finger I18 as indicated in Figure 16, turning the shaft IE5 at each such impingement through an arc of 36, this being suficient to lift the link I58 from the position shown in Figure 13 to its upper position with a high point of the cam i6 1 beneath the follower I62, which throws in'the clutch I553. The outer end of the shaft 538 carries asegmental' shaped member 185 having an arcuate' cam rim-portion I85 for a portion of its circumference and carrying on its inner face an indexing follower I81; It

also carries on its outer face a follower I88 which is positioned to impinge successively upon lobes r89 projecting outwardly from a star wheel 590 also carried by the shaft 55, as shown in Figure 16, this acting to turn the shaft it's through succeeding 36, bringing the high point of the cam I6 3 against the cam follower Iiitand depressing the'link I58 and throwing out the clutch I55. The clutch I55 may be closed by the operator when desired, bypulling outwardly against the tension of a spring I92 on a handle l9] which carries a pivotally mounted latch member I93 which impinges on the star wheel I90 and rotates the cam i154 to clutch-closed position.

Rotation of the follower I37, which as before noted, has been termed an indexing element" acts upon a Geneva wheel I95 secured to the-outer end of the turret i2- as by of screws 59%,

"while the arcuate' cam element !85 operates a turretlocking mechanism to unloc-k it before indexing is to occur and allowing it to lock it after the completion of the indexing. This locking mechanism, as shown in Figure 16, comprises a bell crank lever Z'dllpivoted on the fixed shaft "285, one arm of thislever carrying a cam follower roll 202 against which the outer face of the cam !85 isadapted to impinge during oneportion of the rotation of the member F85, lowering the fol- 'lower 262 from the position shown in Figure 1 6 to the position shown in Figure 17 and rocking a locking dog 2% out from a locking recess of a block Zfififive of which are set into the periphery of the Geneva wheel m5 at equal angularinter- 'vals. The forward edge Bit of the cam portion 18$ effects this releaseof the lock just before the The parts are so timed that thecam lfi has returned the tool holder 2Q to its initialposition shown in Figure 2G with its slot 25. in alinement with the arcuate rib as before: indexing occurs. The first portion of the rotation of the cam: its! acts to retract the follower i2 31 from engagement with one of the edge cams T21 and brings .it

against the cam drummim I 2 2 which acts-v asia he tieuhown e F gure?! es s te' u v e:- tract the holder slide 20 so that, it. is inposition;

for the turret indexing to take place. When this, indexing has been-- completed, the cam i3 'I, ree turning the fulcrum. I25 toward its inner position, first brings the follower I23 against the, hex. succeeding edge cam eleme nt I2I whereuponthe fulcrum reaches its inward position of- Figurev at fastspeed and the cam I3? ceasesv to rotate. The position of the tool holder slide 20 is then un-, der full control-of the edge cam IZI until the cam I3! is again started, which retracts the cam 1 61-, lower I23 against the rim 822 and thereafter moves the tool slide to'the rear position of Figure 2Q where indexing can take place.

The forward motion of each tool slide may be limited positively and independently for each by the-adjustment of checknuts 220 on threaded stop rods 22.!- secured to and projecting rearwardly from each of the tool slide blocks 23 Thesecheck nuts, impinging upon the outer face of the Geneva wheel, limit the forward motion of each of the tool slides. If desired, also, sirn v llai' check nuts 222 which may impinge'upon the inner face of the turret flange It may limit the retracting motion to bring the slots'2d into alinement with the arcuate ribs 33. The turret locking mechanism is normally held in locking position as by a leaf spring 2-25 bearing against the locking arm 295- and it may be held in unlocked position when desired by adjustment of a bolt 22% extending through an arm 22? secured to the bell crank lever 208 which may be caused to bear against an anchor member 228 which secures the fixed end of the spring 225.

It may also be desired, as for setting up the machine, or to retract theiend tools for inspection and measuring the work, to rotate the cam I31 manually. To this end, the outer end of the shaft I5I may be made polygonal as at 23 3 and with it may be engaged a hub '23! of a hand wheel 232', this hub having a hole shaped torecelve the end 235. In the position shown in Figum 13, this hand wheel is reversed from its actuating position and is supported on a hook 2 33 secured to the cover platens, which normally prevents access to the fulcrum bar 25. In the position shown, it protects the operator from ac- 'cidenta1- contact with the shaft end; It is desirable that the extent of this turning motion of the cam I3? belimited. To this end, the shaft I5! is provided with'a wor-rn- 235 journaled there on and connectible bya clutch 2350'to the shaft I51. This worm 235 meshes with a worm wheel 236 journaled one. fixed shaft 231. A stop 238 carrit-zd by this worm wheel 2%- and which may impinge upon one or the other side of. the worm 2-35'limits the angular extent of adjustment. A stop switch located at WEB-normally engagingin a notch in a disk 2M fixed to the worm'wheel' I56 of the clutch I55 as by a rod 2&5, so that when the clutch. I55 is open, which is the. conditionzwhen the shaft I-3S-is stationary, the clutch e235fliisiclosed in conditiomfor thesmanualiturning.

and through change gears 345 and 343.

of the shaft to be effective on the limit switch 249 and the stop 238.

Spindle drive mechanism The drive of the work spindle and cam shaft 69 is derived from a motor 399 (see Figure 3) mounted upon a platform 39! (see Figures 5, 6 and 10) pivoted at one side as on the pintles 392 and supported at its free end on a casing 393 at one side of the end column 2 by an adjustable threaded support 395 engaging a post 395 depending from the platform 39!. This motor has its driving pulley 3; connected as by a multiple v belt 3| with a main pulley 3 l 2 carried by a shaft 3l3 journaled in opposite side walls of the casing 393. The casing 393 with its gear train is separable as a unit from the main portion of the machine frame. The shaft 3!3 has journaled thereon a beveled gear 3% having a brake drum portion 3l5. .The bevel 3i4 may be coupled to the shaft 3I3 by a clutch 3l3 which may be actuated through a clutch arm 39"! fixed to an actuating bar 3!& slidable axially through opposite sides of the casing 393. It may be moved axially by the rocking of a two-part shaft 319 having a double arm 329 connected by a link 32f to a block 322 secured to the bar 333. One portion of the shaft 3!!! projects through the casing 393 and is provided outwardly thereof with an actuating handle 325. This clutch may also be actuated automatically. For this purpose the other portion of the shaft 3! 9 carries an arm 326 provided with a cam follower 321 actuated by suitable cams on a drum 3219 carried by the main control shaft 69, The forward end of this other portion 3!!! also carries an actuating handle 3259.

When the clutch is released, a band brake 323 bearing on the drum portion 3!5 quickly stops the rotation of the bevel gear 3l4. This bevel gear meshes with a bevel gear 339 on a cross shaft 33! provided with a worm 332 meshing with a worm wheel 333 on the shaft 99 and connected thereto through the usual safety device such as a shear pin. This provides the high speed drive for the main control shaft 69.

The shaft 3!3 also drives the work spindle at any selected of three forward and one reverse speed. For this purpose it carries a gear 349 meshing with a gear 34! keyed to the shaft 342 and which meshes, in turn, with a gear 343 journaled on a shaft 344. The shaft 344 is connected through a pair of change gears 345 and 346 within the separable housing 341, with a shaft 348. The shaft 343 carries a sprocket wheel 349 connected thereto through a shear pin 3499 (Figure 10) and over which passes a sprocket chain 359 which passes beneath an idler 35! and about a sprocket wheel 352 on the work spindle 5 (Figure 9). The most commonly used forward speed is that derived through the closing of the clutch 355 by which the gear 343 is connected to drive the shaft 344, the train then being from the shaft 3l3 through the gears 349, 34!, 343, shaft344,

:gears 345 and 346, shaft 343 and through the chain drive to the spindle.

If a higher. spindle speed is desired, as for small drilling or cutting off the work piece from the bar, the transmission may be taken from the gear 349 to the gear 34!, shaft 342, closed clutch 369, gear 36!, gear 362 secured to the shaft 344- If a lower speed is desired, the transmission is from the gear 349, through gear 34!, shaft 342, closed clutch 365 which connects the gear 369 journaled on the shaft 342 to the shaft 342, the gear 391 i ii secured to the shaft 344, and through the change gears 345 and 346.

Where a tapping operation is employed, it is necessary to revers the direction of rotation of the spindle in order to retract the tap from the work. The drive in the reverse direction is ac-; complished by closing the clutch at 319, the train then being from the gear 349 to the gear 34!, shaft 342, the chain 31! passing over a pulley 312 (Figure 7) fixed to the shaft 342 and over a second pulley 313, clutched to the shaft 344 by the clutch 319, which thus drives the shaft 344 in the reverse direction. The clutches 365, 355, 399 and 319 are actuated by yokes carried by pivoted arms 389, 33!, 382 and 383.

A low speed drive for the main control cam shaft 69 is derived from the spindle. To this endthe spindle is provided with a sprocket wheel 385 which is connected through a sprocket chain 396 with sprocket wheels 399 and 389 on a pair of shafts 399 and 39! (see Figures '2 and 9). As shown best in Figures 5 and 8, the shaft 399 carries a gear 392 meshing with a gear 393 on a shaft 394, while the shaft 39! carries a gear 335 meshing with a gear 396 fixed to the shaft 399. The sprockets 388 and 389 are connected with the shafts 399 and 39! by roll clutches which permit the drive to these shafts only in opposite directions. Thus when the chain 386 is traveling in a direction to rotate the shaft 399, it is ineffective on the shaft 39!, the transmission then being from the shaft 399 through the gears 392, 393 to the shaft 394. When the chain 386 is moving in the opposite direction, the shaft 39! is being driven in the reverse direction to the drive of the shaft 399 while the shaft. 399 is not then being driven, and the transmission is then through the gears 395, 396, 392 and 393 to the shaft 394. The shaft 394 is thus driven in the same direction, regardless of the direction of motion of the chain 386. The shaft 394 has a worm 399 thereon which drives a worm wheel 499 journaled on the shaft 33! and adapted to be connected thereto through a one way roller clutch 49! and a positive clutch 492. The roller clutch provides for overrunn ng of the shaft 33! when it is connected for the high speed drive from the gear 339 ven though the positive clutch 492 be closed, and the positive clutch 492 provides for drive from the worm wheel 499 when the bevel gear 339 is not being driven. This low speed positive clutch is controlled by the swinging arm 493 carried by a rock shaft 494 and which may be controlled from the exterior of the machine by a handle 495 at the'front of the machine. The rock shaft 494 may also be connected through an arm 493 and a link 491 with an arm 499 on a rock shaft 499 provided with an actuating handle 4 I9 at the back of the machine.

The control of the speed and the direction of rotation of the spindle may be effected automatically in accordance with the requirements of the cycle of the machine. As shown these are controlled by cams on two cam drums 429 and 42! carried by the shaft 6. Cams on the drum 429 control the angular position of a rock shaft 422 having a cam follower 423 actuated by these cams, the shaft 422 also having a handle 424 outside of the machine casing by which it can be actuated. The opposite end of the rock shaft 422 has fixed thereto a double rock arm 425 (see Figure 6) having a pair of angularly related ways 42'! and 428. Within the way 421 rides a follower 429 on an arm 43!! connected to the clutch arm 393, both of these being fulcrumed at 432. The

" one time.

7 way 428'has :riding therein a oi1ower-43 carried -by an arm 436 connected to the clutch arm 38!),

a both "being fulcrumed-l-at 431. Rocking not the ates the slow speed clutch-arm -38ll,while it -is substantially ineffective to rock the arm-430 in view of the angularity-of the way 421 with rela- -tion to that of the arm 430. Rocking-f the {member 425 in clockwise direction from the position-shown exerts a substantial rocking action on the arm4-30 to=actuate the clutch arm-383 while it is substantially ineffective-to rock the arm 435'due-tothe-angu1ar relation of this arm to the way 428. The cams on the drum 42I act similarly to .rock a Frock-shaft 44!] which also is lprovide'd withra.follower .441 and with an actuat- -ing handle 442 outside .of the machine. The 'inner end of thelvshaftilhill is provided with a ldoub'lelarm member 4429 having tarpair of pins :443 and .444, which ride in slots-.445 and l44'6, re-

' flspectively inlarms 4'41 and 448 connected to the clutch arms v382 and 38l respectively. Rocking of the member 442 counterclockwise from the position shown' is substantially ineffective to rock thearm 4147., butfis effective to rock the arm448, while rocking .of the member 442.cloclewiseroclcs the arm 441, thus moving the clutch arm 382 while-it substantially ineffective to lrockrthe arm -4.48.- Thus by rocking either of the shafts .420 and 7440 in one .or the other direction, the control clutches determining the .speedandthe direction of rotation of the. spindle are l-actuated. "The shafts are alsointe'rlocked so that when any one of these .four clutches is 'a'ctuated, .a1l :of Jthe others are held against actuation Eloy the interlocking connections between the itwo rock shafts 1422 and 440 with their actuating mechanisms. \The 'interlocking'of the-shafts Mlland 440 ,is flpro'ducediby mechanism best shown .in Figures,5,f1' 7,'and8. Each oftheshafts 422 and 443 has fixed "thereto .anedge foam such as 450 and 451, each *of these cams being circular for the greater portion of its gperiphery, but provided with a flat at452 and4513. "Riding on the two shafts 422 and 4401s a member .1454 "slotted at its ends. as at 455 to engage iover 'andbe supported by the shafts 422 and 449. Between these shafts the member 454 is provided with oppositely facing cam engaging "facesM45-6 "and 451, .each facing one ofthe'cams 459 and 451. These faces 455 and 451 are sospaced with'lrelationr to the shafts 4'22 and ,440 and the cams thereon that when one of these-member faces is engaged by a corner adjacent to the :circular portion of one of the'cams '45lIand'45L'as shownin Figure 8a, which isthe situation whenever the corresponding shaft is turned out of neutral position byits actuating cams, the member 454 is pushed over toward theopposite shaft, bringing its face against .thefflat of the other cam, thus preventing this shaft from being-rocked out of itsneutral position while the other r'shaft remains -out;'of neutral angular position. Thus only on'eofthe clutches which controls the speed or, direction of rotation of the workrspin'dle may he 'cl'ose'd at any llfifachizeiop'emfzon At theista'rto'f :a machinexcycle, workfitll which is carried within "the hollow spindle :5 :projects forvlardly therefrom to the desired extent for the machining operations as shown in Figures 1 and :4,"this extent 'havingibeen determined bythes'e'tting ofthestocl; stop which *justrloefore the close of the cycle was moved into operative position for the feeding .of the worhanjdthen re'movedto its inoperative position shown .in Figures land-f4. The lever H4 is then in the position with its cam follower 23 engaging ane'dgecam I2! adjacent to beginning of'its contact therewith and its fulcrum 535 is in engagement withthe block 140 of the cam I37, as is shown in Figure :15. The upper tool carrier slide 211 has thus been moved forwardly toward the work from its retracted position where the :turret might be indexed, and the indexing mechanism is in the position-shown in Figure 16 with the turretloc'hed. The main cam drum it and the work spindle are then started to rotate, the motor 545 heing in oontinuous rotation during theentire time of operation of the machine, and the various tooling operations are started upon the work, these'depending upon the setting of the cams on the several cam drums which control the motions of the side tool slides :and the end working tools. The end working tool is given its icrwardtooling motion toward the work by rocking of the lever l24 by motion of itsactuatingfollower 123 inaceordance with the contour of its controllinglcam l2l, and "this action continues "during-the rotation of the shaft 5i? until the edge cam I 2| passes the desired amount past the lever follower I23. When this has occurred, the clutch cam I64 "is rotated by engagement of onelof the fingers III on a finger N8 of tlie'shaft lfi5,-closing the'clutch 655 and starting the rotation'of "the secondary shaft 538 and the cam l3? thereon. The'a'ction of the cam path l136'lof this cam L3'iiimmediate1y retracts the fulcrum slide 1226 toward the right-as viewed in Figure 4, and swings the follower 123 against the rim 122 oofsthe cam 'drum lzfl into the position shown in Figure 19. .Assoon asxthis'cam follower bears :againstthe rim I22, furtherrotation of the cam I31 acts quickly .tolpullthe'tool slide 23 back to the p sitiOn-of-FigureZO where its notch .24 is in alinement with the space between the flanges?! and 2'8. :At'about'thistime the cam portion i8 5 on thecsegment :I'85;engages the follower262 :of :the turret locking arm 1-260 and releases this armywhereuponathe indexing member 2 engages jinsone @f thefslots of the Geneva wheel and-indexes the turret. :Further charge and produce the feed motion'of the tool agai .51; the work. Bythertime-"the'camslfil has completed its single revolution, the follower 488 on the'seginent l85 has :struckcneeof the points l 89 of the star Wheela'ndt disconnected the clutch E 55 and :thusstoppeii the rotation of the secondary shaft A38. The t-tooling operation then continues with the sec'ondaxial lt'ool. This" oper- .:ation is repeated often as 40116 :of the fingers l'll starts the rotation :of itheslseeondary shatt,

:r'etracting one of the'zt'ools and :zcaus'ing indexing ofthe turretiand bringing.a subsequeritaxial tool :into position. It will be noted that whenever-one cam i121 ismovi'ng out of a'ctionand a succ'eeding cam 1-2! is moving into factiomthe' follower 23 is in engagement with the cam rim 122.

Thus

, sm'oothcontinuity from one cam 1:21 'to'thetnext is :not necessary, :and they "may .zpresent 'a jagged or saw tooth effectif this iszdesiiable, Zt'o properly position SIICCES'SiVElYiDIGSIltBd iaxial tools.

At any time during the operation'of the end tools, the side working tools may be operated in accordance with their desired sequences, and at suitable times in the complete cycle, the speed of rotation of the spindle is changed as may be desired by the nature of the tools working thereon. Whenever the direction of rotation of the spindle isreversed, of course the side working tools will be out of operation.

During the retraction of the axial working tools, it may be desired to speed the rotation of the cam shaft 60 and this is done by the actuation of the clutches which control the drive of this shaft either from the high speed drive or from the low speed drive, as previously described.

Near the end of the cycle of operations when all of the end Working and side working tools have completed their cycles of operation, the last side working tool cuts off the completed stock while the axial working tools are in retracted positions, the work is unclamped in the spindle and the stock is fed forward against the stock stop which has been moved into' operative position. The stock stop is then retracted, and the machine is in the condition for the beginning of the next complete cycle of operations.

From the foregoing description of certain embodiments of this invention, it should be evident to those skilled in the art that various other modifications and changes might be made with out departing from the spirit or scope of this invention.

I claim: 1. In combination, a work holder, an indexing turret, a plurality of tool holders carried by said turret in position for tools on said tool holders to be moved sequentially into and out of operative relation to work on said work holder by indexing of said turret, a main control shaft,

a cam drum on said main control shaft having edge cams thereon and an outstanding rim spaced from the active faces of said earns, a secondary shaft, power driving means for said shafts, a lever having an actuating arm, a follower on said arm movable along said drum between said edge cams and said rim, a member on which said lever is fulcrumed movable transverse to the fulcrum axis and substantially parallel to said main control shaft, a cam on said secondary shaft moving and controlling the position of said fulcrum member, means for rotating said main control shaft to cause said edge cams to move said lever and impart working motion to the tool holder in operative position while said secondary shaft is stationary, means controlled by said main control shaft at the end of said working motion torotate said secondary shaft thereby to move said fulcrum to bring said follower against said rim and to return said tool holder to a starting position, and means actuated by continued rotation of said secondary shaft thereafter to index said turret to bring a succeeding tool holder into operative relation to said lever and then to return said fulcrum member to its active position with said follower in controlled relation to one of said edge cams and to then stop the rotation of said secondary shaft.

2. A machine of the class described, having an indexing tool carrier provided with a plurality of ways extending parallel to its indexing axis,

a tool holder reciprocable in each of said ways, a tool holder actuator, said actuator and holders having portions interengaging when the portion of each holder is moved to a predetermined angular position about the indexing axis by the indexaxial position, a stationary member with which each of said tool holders engages while out of said predetermined angular position for retaining said tool holders in said axial position means for moving said actuator to move a tool holder in said angular position away from said axial position while said carrier is in an indexed position and for returning said tool holder to said axial position before a subsequent indexing of said carrier, and means for indexing said carrier.

3. A machine of the class described, comprising an indexing carrier provided with a plurality of ways extending parallel to its indexing axis, a holder reciprocable in each of said ways, and having a slot in its face turned outwardly from said axis, said carrier having a peripheral slot with which said holder slots may register, a stationary member engaging in said slots and provided with an opening at one angular position with which said holders register serially as said turret is brought into indexed positions, said opening permitting the holder registering therewith at any time to be moved in its ways to bring its slot out of registry with said peripheral slot, means actuable to move each holder when in such registering position to bring its slot out of registry with said peripheral slot and thereafter to return said holder to said registering position, and means for indexing said turret.

4. In combination, members comprising a work holder and a tool holder mounted for relative motion to cause a tool on said tool holder to act on and retract from work on said work holder, a support mounted for reciprocatory motion, a lever fulcrumed on said support and having one arm connected to one of said members and another arm provided with a cam follower, a main cam shaft, a secondary cam shaft, a cam drum carried by said main cam shaft, an edge cam carried by said drum, said drum having a rim spaced from said edge cam and within which space said cam follower rides, a closed cam on said secondary cam shaft, a follower for said closed cam connected to said support, means for intermittently rotating said secondary cam shaft to move said support and bring said lever cam follower into and out of engagement with said edge cam and rim and said movable holder toward and from operative relation to the other of said holders, and means for rotating said main cam shaft.

5. In combination, a work holder, an indexing turret, a plurality of tool holders carried by said turret in position for tools on said tool holders to be moved sequentially into and out of operative relation to work on said work holder by indexing of said turret, a main control shaft, a cam drum on said main control shaft having edge cams thereon, a limit stop spaced from the active faces of said cams, a secondary shaft, power driving means for said shafts, a lever having an actuating arm, a follower on said arm movable along said drum between said edge cams and said stop, a member on which said lever is fulcrumed movable transverse to the fulcrum axis and substantially parallel to said main control shaft, a cam on said secondary shaft moving and controlling the position of said fulcrum member, means for rotating said main control shaft to cause said edge cams to move said lever and impart working motion to the tool holder in operative position while said secondary shaft is stationary, means controlled by said main consaid secondary shaft.

6. in combination, members comprising a work holder and a tool holder mounted -for relative "motion to cause a tool on said tool holder to act on'and retract iromwork on said work holder, a support mounted for reciprocatory motion, a 'l-ever f ulcrurned on said support and having one arm connected to one of said members and another arm-provided with a cam follower, a main cam shaft, a secondary cam shaft, a cam drum carried 'by said main cam shaft, an edge cam carried .by said drum, a stop spaced from said edge :cam and within which space said cam follower rides, a closed camon said secondary cam shaft, a follower for said closed cam connected to said support, means :for intermittently rotating said secondary cam shaft to .move said support and bring :said ilever cam follower into and out of engagement with said edge cam and stop and said movable holder toward and from (operative rel tion-t th th r aid ho d rs and ne ssrtsrmts CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name D t 7.25A38 ridley Amt 1 190 857 9 Newton June 2.5, .1907 41 1 9 252 SeD-t 26, 9,1 1,215,000 Cone Feb. 6', 19.17 1,484,604 ohapman Feb. .19, 11,924 51 5 35 War N v- 11 $1 7 7 0 E s he Dec. 29, 19.2 1,765,592 Kinsmen: e June 2 30 IJBBAZZ D issne e e J n- 13 3' 2o ,1 6 .2' Lo ely Ju -v 119.3 2 9 15% ixon raw-"1T"- J .9 .193 2 118,01 Mo om =7 M y 27, .193 2,169,780 WlL O ug. 7175, .1 9 2 70 6 3 .Dr ssne Au '22, 11,93 mars? B illa ui e 41s 19: 2,339,140 Boillat 7., Jan. 1,1, 19.44 23%415 r M m-11 FOREIGN PATENTS u e Coun gate 

